Rotary vane fluid pressure machine



June 27, 1950 w, l BROWN ROTARY VANE FLUID PRESSURE MACHINE Filed Dec.27, 1943 3 Sheets-Sheet 1 June 27, 1950 w. F. BROWN 2,512,593

' ROTARY vANE vFLUID PRESSURE MACHINE Filed Dec. 27, 1943 s sheets-sheet2 BY l d m? v frag/v if June 27, 1950 Filed Dec. 27, 1 945 W. F. BROWN IQOTARY VANE FLUID PRESSURE MACHINE 3 Sheets-Sheet 3 BY im M170/V57Patented June 27, 1950 ROTARY VANE FLUID PRESSURE MACHINE William F.Brown, Flushing, N. Y., assignor, by direct and mesne assignments. ofthirty per cent to Philip S. McLean, Bloomfield, N. J., ten per cent toFrank L. Davis, College Point, and ten per cent to Howard D. Flicker,Queens Vil-I lage, N. Y.

Application December 27, 1943, Serial No. 515,824

1 Claim.

The invention herein disclosed relates to fluid `pressure machines,particularly rotary pumps of 'the type disclosed in copending patentapplication Ser. No. 454,775 iiled August 14, 1942, now Patent 2,370,934issued March 6, 1945. A

A Special objects of the invention are to provide a rotary pump of thepositive displacement type, which will have large volumetric capacity,create vdirect flow of liquid without setting up turbulence and producesmooth continuous flow free of pulsation.

Further important objects are to provide a ma-A chine of few, simple,sturdy parts, operating on their own centers, free of reciprocatingmovements, which will be light in Weightv and small, for the workaccomplished, which will operate on a low power factor and which can beoperated emciently at slow speeds, as well as the higher speeds andwhich can be utilized to develop desired pressures at different speeds.

Other desirable objects and the novel features by which the purposes ofthe invention are attained will appear in the course of the followingspecification.

The drawings accompanying and forming part of the specificationillustrate certain practical embodiments of the invention. Structurehowever, may be modied and changed as regards the present disclosure,all within the true intent and broad scope of the invention as will beapparent from the following specification and claim.

Fig. 1 in the drawings is a vertical sectional view of an embodiment ofthe invention, this view being taken on substantially the plane of lineI-I of Fig. 2.

Fig. 2 is a vertical sectional view at right angles to that shown inFig. l and taken on substantially the plane of line 2-2 of Fig. 1.

Figs. 3 and 4 are broken sectional` details showing inlet and outletport constructions for the .inner pumping chamber and takensubstantially on lines 3-3 and 4-4 of Fig. l.

Fig. 5 is a broken horizontal sectional view on substantially theplaneof line 5-5 of Fig. l.

Fig. 6 is a top plan view of the machine.

Figs. 7 and 8 are elevations illustrating opposite sides of the machine.

Figs. 9 and 10 are vertical sectional views illustrating modied forms ofthe invention.

As shown particularly in Fig. 1, the body or casing III, of the machine,is formed with a cylindrical working chamber I I, and the piston blades,in this case, three in number, designated I2, I3, `il, are mountedconcentrically within this chamber. rotating on a stationary post l5,carried by and projecting from the back wall I6, of the chamber..

The front wall I1, is shown as separately formed and removably securedin place and as carrying the bearing I3, for the shaft member I9. Thecenter 20, of this shaft, as best shown in Figs. 1 and 2, is offsetabove the blade center and the purpose of this is to support thecylindrical rotor 2l, which it carries, in running sealing engagementwith the upper peripheral portion of the pump chamber at 22, and todefine the crescent shaped pumping space 23.

The cylindrical rim portion of the rotor has three equi-distantlylocated slots 24, 25, 28, through which the rotary piston blades projectinto correlation with the walls defining the crescent-shapeddisplacement space.

Inlet and outlet passages are provided in the casing, opening into thedisplacement chamber at opposite sides of the tangential sealingengagement 22, between the rotor and surrounding chamber.

The inlet 21, is formed with two ports or passes 28, 29, opening throughthe peripheral wall of the cylindrical chamber in angularly oiIsetrelation, one in advance of the other. The first port 28, is locatedrelatively near the sealing line- 22, in position to be uncovered byblade I3, shortly after it passes the seal between inlet and outletsides of the pump. The second port 29, is located far enough in advanceof the iirst to remain open substantially up to the maximum displacementestablished within the crescent chamber.

Similarly, the outlet 33, is shown as having separate discharge ports3I, 32, angularly offset. vthe first in this case located to be openedat sub stantially the instant of maximum displacement and the second toremain open after the first is closed and while the final fraction isbeing swept out of the chamber.

In the full line position of the parts appearing in Fig. 1, the forwardblade I2, is drawing from both ports 28 and 29. In the next positionrepresented by dot and dash lines, the blade I3 has closed the rst inletport 28, so the forward blade I2 is drawing through the forward port 29,and will continue to so operate until the dash line position is reached,at or about which moment of maximum displacement volume, the blade I3will close the second inlet port 29. Approximately at this instant. theforward blade I2, will uncover the first outlet port 3|, to enable thefollowing blade I3 to start discharge through that port. As the partsreach the dotted line position, blade I3 continues discharge through thefirst outlet port and then as the forward blade reaches the full lineposition where blade I4 is shown, both outlet ports will be fully openand the second port will remain in service for suillclent time after theiirst port has been closed, to enable substantial clearance of theremaining portion of the chamber. In its further travel, the blade atthe i4 position will aid in maintaining the tangential seal between therotor and surrounding pump wall.

The successively acting ports enable the blades to operate at besteiiiciency, to completely illl the chamber and to start dischargeimmediately the chamber is filled, thus assuring smooth continuous flowand maximum volume, substantially free of pulsation.

The eccentric disposition of the blades within the rotor eiectsdisplacement within the rotor, substantially the reverse of that eiectedin the crescent chamber and such displacement is utilized in the presentdisclosure by providing sel)- arate angularly offset inlet ports 33, 34,opening from a passage 35, through the back wall of the casing into theopen end of the rotor, the first at a point to be uncovered when thespace between adjoining blades commences to enlarge and the second at apoint to be closed when the space between adjoining blades has reached amaximum. The passage 35, is shown extending back in a loop to a port 35.branching from the main inlet passage.

Outlet ports 3l, 38, are shown provided in the back wall IS, at theopposite side from the inlet ports, in position, the first to open whenmaximum volume between adjoining blades within the rotor is attained andthe second to be closed when the displacement space between adjoiningblades within the rotor is substantially at a minimum. The interior-lylocated outlet ports are shown connected by branch passage 39, leadingto a discharge port 40, opening into the side of the main outlet 30.

The interior pump passages 35 and 3i) may be cored or otherwise formedin or on the back wall of the casing or they may be provided by separatepipe connections. Further, instead of being connected with the main pumpinlet and outlet, they may be connected with other` liquid or fluidholders.

As shown particularly in Figs. 3, 4 and 8, the inner pumping passages,provided by conduits 35, 39 and the ports 33, 34 and 3l, 38, may becurved or directed in the general direction of rotation, so as to passthe iiuid freely without disturbance or tubulence.

By utilizing the space within as well as the space without the rotor, amaximum pumping effeet is obtained and a substantially continuous andpulsationless flow can be maintained with maximum eiiciency and lowpower consumption.

The rotor and the three blades are the only moving parts and these allturn on their own centers. The blades may be driven by their engagementin the slots, or if desired, through linkage connections with the rotoras disclosed in the copending patent application above identified. As afurther possibility, the blades may be driven from a centrally locateddrive shaft and the rotor be separately mounted and operated through theslot connections or by linkage such as mentioned.

Various other modifications are possible, but the simple form ofconstruction illustrated, has many manufacturing and operatingadvantages. As shown in the several views, the rotor may be formedsimply asl a hollow cup on the end of a shaft, with slots cut through tothe solid back wall 4I, of the rotor and the inner face of this wall maybe iiush with the adjacent side wall 42, of the crescent chamber,substantially as indicated in Fig. 2. With such construction, the bladesmay be plain straight sided elements, closely fitting in the cup of therotor and coacting with the surrounding walls of the crescent chamber.The hinge loops of the blades may be oiset to interlock substantially asshown in Figs. 2 and 5, where one blade such as I2, may have two outerhinge loops 43, another blade I3, the two loops 44, to stand inside theouter loops and the third blade I4, a single center loop such as 45. Therotor is shown turning in a seat 46, in the front cover, acting partlyas a bearifg and seal for the shaft and serving to bring the inside wallof the cup formation into flush relation with the front wall 42 of thepump chamber.

To take up space in the inner chamber not actually serving for pumpingpurposes, the hinge post I 5, and hinge loops of the blades may be madeof larger diameter, as indicated in Fig. 9, so as to occupy practicallyall of the space within the rotor, between adjoining blades defining theminimum volume space.

To complete this effect or as a substitute for the large diameter post,the rotor may be contoured on its inner wall between the blade slots asindicated at 4l', to substantially lill the space between blades in theminimum volume position, that is, when two adjoining blades, such as thetwo blades I3, I4 at the bottom in Fig. 9 are in closest conjunctivityto the surrounding Wall of the rotor.

As a further possibility, the blades may carry llers 48, on theiropposing faces, which in the minimum volume position will come togetherto substantially ll in this entire space as indicated in Fig. l0.

The provision of the inner pumping ports and passages in the back wallof th-e casing is of advantage in providing all the fluid connections onthe main body of the machine. Also, the mounting of the pivot post onthe back wall is of advantage in enabling the machine to be assembled bysimply dropping the blades into position over this post and then, whilethe blades are so held,

engaging the slotted rim of the rotor over the blades. It iscontemplated however that these relations may be reversed, that is, theinner ports be located in the cover Wall, and or the pivot post bemounted on the cover and the rotor be journalled in the body portion ofthe machine.

While disclosed primarily as a pump, it will be realized that featuresof the invention are applicable to other than strictly pumpconstructions and the disclosure accordingly is to be so considered andthe claims so construed.

The double inlet and outlet ports separated in the angular relationshown are highly eifective in providing maximum pumping capacity, partlybecause of the fact that the solid wall surfaces between companion portscooperate with the blades in the travel of the blades between ports. Inthe construction shown, all three blades are Working, that is,performing useful but different pumping functions at all times. Thesecoactive eiTorts of the three blades accomplish a maximum pumpingability with the fewest number of parts and renders any additionalblades or parts unnecessary or possibly even disadvantageous.

For 4operating on some fluids or liquids, where uninterrupted ilow isparticularly important, or

for other causes, some overlap may be provided in the portingarrangement, so that an outlet port will be open at one side actuallybefore the inlet port has been closed at the opposite side.

What is claimed is:

A rotary pump comprising a casing having a cylindrical chamber, acylindrical rotor of smaller diameter journalled eccentrically in saidchamber in tangential sealing relation with the surrounding wall of saidchamber and forming in conjunction therewith a crescent-shapeddisplacement space, said rotor having equi-distant radial slots openingthrough the peripheral portion of the same, radially extending rotarypiston blades pivoted concentrically in said cylindrical chamber andextending through said slots into cooperative relation with thesurrounding wall defining said crescent-shaped space, the casing havinginlet and outlet passages opening into the ends of said crescent shapedspace at opposite sides of the point of tangency of the rotor, saidinlet having separated ports located one in advance of the other in thedirection of rotation of the blades, and positioned the one in advanceto remain open to the crescent space between two adjoining blades up tosubstantiallyv the maximum volume of the crescent space betweenadjoining blades and to be closed to said last named space by the secondof said blades substantially at theinstant of change to decreasingvolume space and the outlet passage having a port positioned to beuncovered to said last named crescent space by the rst of said twoblades substantially at said instant of changing to lesser volume, thefollowing blade during said port controlling movements of the other twoblades traversing the tangential sealing portion of the chamber betweenthe inlet and outlet passages and said casing having spaced,interconnected inclet ports and spaced, interconnected outlet portsopening into the space within the rotor at opposite sides of the centerof rotation and into minimum and maximum displacement areas deii'nedbetween adjoining blades within the rotor.

WILLIAM F. BROWN.

REFERENCES CITED The following references are of record in the file ofthis patent:

UNITED STATES PATENTS Number Name Date 22,832 Thomas Feb. 1, 1859797,621 Smith Aug. 22, 1905 812,688 Sharp Feb. 13, 1906 1,221,333Killman Apr. 3, 1917 1,558,696 Marion Oct. 27, 1925 1,607,383 AurandNov. 16, 1926 1,670,229 Balsiger May 15, 1928 1,737,942 Pagel Dec. 3,1929 2,001,011 Brown May 14, 1935 2,033,218 Yirava Mar. 10, 19362,233,269 Napolitano Feb. 25, 1941 2,370,934 Brown Mar. 6, 1945 FOREIGNPATENTS Number Country Date 21,340 Great Britain Oct. 7, 1899 133,555Switzerland Aug. 16, 1929 323,564 France 1902 395,492 France 1908

